High-speed bearing



' Aug. 1, 1944.

GH SPEED BEARING 2 sheets-sheet4 1 l Filed Nov. l, 1941 .wmf T .QN mmf .QN www mi MN .WAB

Aug- ,1, w. MESSING-ER ET AL .2,354,870

HIGH SPEED BEARING Filed Nov. l, 1941 2 Sheets-Sheet 2 IN VENT OHS N4 E my M ER o M n MNYA Mm?. M.

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Patented ug. 1, 1944 HIGH-SPEED BEARING William Messinger, Philadelphia, Pa., and Alexander Shayne, New York, N. Y.

Application November 1, 1941, Serial No. 417,514

3 Claims.

This invention relates to improvements in high speed bearings vfor rotors, such as shafts and tubes or cylinders, whether rotating about a vertical or horizontal axis, and has for its' object the elimination of nutation and excessive vibration .when rotated at high speeds. It is well known that rotors of this type require a substantial clearance between the rotating object and the supporting bearing suicient not only to enable an oil film to build up for the vpurpose of supporting the rotor, but also to supply enough oil to lubricate and cool the bearing and also to compensate for variations due to ,the different temperature coefficients of the various elements employed and to the different temperatures in various parts of the elements comprising the system. This clearance varies with the diameter of the'journal, unit pressures on the bearing, viscosity ofthe oil, peripheral speed of the rotating element, etc., and may be as high as .025 `inch on each side between the shaft and the bearing. Such clearance creates a, condition in the supporting structure which permits an oscillation of I `the rotor to build up which reaches dangerous proportions'at high speed and definitely limits the rate of rotation of such revolving members. This condition kcan arise because a slight unbalance is almost always present, and an un- .balance even to the extent of one ounce in a rotor weighing many tons, can set up an oscillation of its own. These two factors, therefore, create a condition which gives rise to excessive vibration and makes it impossible to rotate shafts or rotors of large size and weight at high speeds.

rality of small, exibly supported bearing blocks adapted to engage the rotating object, as shown in Patent No. 2,003,316, granted June 4, 1935, A. E. Schein, inventor. The advantages claimed 5 for this construction are, first, that since these bearing blocks are flexibly supported, it is not v necessary to provide theplarge clearances which were heretofore essential when the entire peripheryy of the bearing formed the |bearing structure.

Thus the blocks could be initially positioned close to the rotor surface, for example, within .002 inch, and thus the large clearance heretofore deemed necessary is avoided and one inherent cause for the oscillation of the rotor is completely eliminated. As the oil film builds up, the flexibly held bearing blocks yield only sufficiently to permit this oil film to form, and i'f excessive loads are suddenly placed upon any given/portion of the bearing, the particular bearing block or blocks would yield by compressing its` supporting spring.

The other advantage claimed for this construction was that if the rotor itself were out of balance and tended to rotate about a different axis from the axis of the bearing, the flexible bearing blocks would permit such rotation, and vibration thus ment of the axis about which the rotor revolves,

causes not a fixed'linear displacement of the axis of rotation, but rather by reason of the fact that all the bearing blocks around the periphery are flexibly mounted, permits this axis of rotation to Thus, for example, in the case of a machine 3, travel in a circular path, although considerably wherein paint is sprayed upona rapidly rotating/f cylinder for breaking up the paint in the form of a mist, it is desirable to rotate this cylinder at as high speed as possible in order to obtain the most eective action of breaking up the paint when the latter strikes the cylinder. This cylinder is in the form of a drum approximately 12 inches outside diameter and 115 inches long, and heretofore no bearing of known type has been found which could withstand a speed of more than 1800 R. P. M.,and even at this rate of rotation such bearings were found to have a very short life. By this invention a speed of 4.000 R. P. M. for the drum just' specified has been obtained without deterioration of the bearing over a long period of time. t

It has been proposed heretofore tosolve the above `problem by providing within the circular bearings at a plurality of points, preferably symmetrically disposed around the periphery, a pludamped by the springs, in other words, in a nutating movement which consequently tends to set up vibration in the rotor. 'I'his invention, therefore, has for its principalobject the v'improvement 40 of a high speed bearing of the type which employs flexibly' mounted bearing members, which, however, will reduce vibration. 'This in `turn will permit the rotor to be driven at much 'higher speeds than heretofore without damage to the bearing, as, for instance, in the example cited above wherein a rotor which by virtue rof its construction could not'be well-balanced and'which had previously had a, maximum speed of rotation of 1800 R. P. M. with damage to the bearingswithin a very lshort time, is now being operated at y4,000 R. P. M., in its original condition of unbalance, 4over a long period of time'with no wear on these bearings.

Further objects and advantages of this invention will become apparent in the following de-v tailed description thereof.

In the `accompanying drawings,

Fig. 1 is a vertical section through a bearing embodying this invention and shown asapplied to the support of a cylindrical rotor.

Fig. 2 is a verticalsection taken substantially on the-line 2-2 of Fig. 1, shown positioned within a drum connected thereto.

Fig. 3 is a view similar to Fig. 2 showing a modined form of the invention adapted to take up axial as well as radial thrusts.

Fig-Lis an assembly view of a grinding machine embodying this invention.

Referring to the drawings, this invention is shown in Figs. 1 and V2 as applied to the support of a large drum or cylinder,i\n which case the bearing is mounted on a xed shaft extending through the drum and the drum is rotated while being supported on its inner periphery. However, this invention appliesfalso to thecase where rotating shafts are supported inside the bearing which then surrounds the rotating shaft and engagesthe periphery of the shaft, as disclosed in Figs. 3 and 4.

In the form of the invention shown in Figs. 1 and 2 of the-drawings, a large drum I0, which may be the drum of the device hereinbefore described, viz., a rapidly rotating drum upon which paint is sprayed for the purpose of breaking up\ the paint in the form of mist which is then deposited upon a suitable surface such as paper ortextile, is supported upon the bearing forming this invention. The drum is rotated at high speed by any suitable means, not shown, such as a' motor drivingzthrough.gearing `fixed to the drum.l

The drum supported `upon the bearing by fixed against rotation in suitable standards, not shown. The support for the shaft I5 is such that it maybe disengaged at one end to permit the drum tobe assembled thereon.

Thering I3 and therefore the drum I0 is supported for rotation upon the-sleeve I4 which car--` ries in its outer periphery a plurality of bearing linings or bearing-metal pads I6 and I8, preferably positioned symrnetrically around the periphery. The linings I6 are flxedly positioned within grooves Il while the linings I8 are positioned within cylindrical bores extending through the wall of sleeve I4. Each bore 20 is provided with an enlarged inner shoulder 2| within which is fixed, as by welding, a plate 22. This plate forms a stop or limiting position for the ange 23 of a lcylinder 24 slideable within the cylindrical bore 20. 4A compression spring 25 rests at one end against xed plate 22 and at the other end on the closed end 26 of the cylinder 24. The bearing linings I8.are fixed to the outer surface of the closed ends 26 of cylinders 24, and the springs normally press the cylinders 24 outwardly un "til the flanges 23 reach the outer ends of their retaining grooves. At this point there is a clearance 29 which may be of any desired magnitude, depending upon the particular application of the invention, and in the example which we have chosen this clearance is approximately .012 inch. With the parts in this position, the linings I3 extend outwardly beyond the outer periphery of sleeve I4 to such extent that when ring I3 is positioned thereover the entire clearance between ring I3 and sleeve I4 is taken up by the linings. This clearance is. as heretofore stated, small, on the order of .002 inch, Just sufllcient to permit the supporting oil film to build up. When, however, vthe load is applied to these linings I3, the springs ported linings Il.

rotor to be displaced from'Q vto O', the axis 0" would, by reason ofthe fact that all of the linings cated by the arrows, which a path of nutation j or oscillation which causedj'a `vibiation to be set up in the rotor at highspeeds. By making certain of the linings nxed vwinne'certain others arei f;

a yieldable, this condition is. avoided, for even` if the unbalance of the/rotorA lcauses the axis of.; rotation to be displaced 1 frn O' to O', it cannot I travel in the nutatingvpath O shown by the arrows, by reason of the fact that the lir'iings"v I6' are fixed Thus, the tendency of the rotor to vi-f.

brate or oscillate due to unbalance which has previously been present in radial bearings having all of the bearing points yieldably mounted, is re'- duced. It is obvious that this result is obtained by reason'of the fact that certain of the bearing pointsare flxedwhile others are yieldable. While there are shown two fixed bearing points, it will be understood that more or less than two may be .employed providingthat at least one bearing point is fixed. Also, while there are shown two yieldably and flexibly mounted bearing points, more or less than two may be employed. Prefpreferably so positioned as to carry the weight of the rotating member. In the form of the invention shown in Figs. 1 and 2, the bearing is inside the rotating tube and therefore the upper linings I6 and I] are fixed since they carry the weight of the tube.

In the Fig. 3 form of the invention there is a central rotating shaft I5', and the'bearing members surround this shaft so as to engage the periphery thereof. In this case the weight of the rotating shaft will be carried by the lower linings I6', while the upper linings I6 are yieldable.

The form of invention disclosed in Fig. 3 is particularly applicable to that type vof device wherein a rotating member is subject not merely to high radial thrusts but must be held against axial thrusts as well. Thus, in the case of the grinding machine disclosed in Fig. 4, there is a grinding wheel 53 carried at one end of a rotatagainst axiai thrusts, otherwise the width or the groove which the grinding element will cut will be indefinite and inaccurate. The shaft Il carries a balancing fly-wheel 52 at its other end andl is journaled by two bearings contained in housings 53 and 54, while motor elements 55 surround the shaft which carries the motor armature. The type lof bearing disclosed in Fig. 3 may be employed in both housings 53, 54, but if desired one of the bearing elements such as the element in housing 54 may be of the type disclosed in Fig. 3 designed to take up `axial and 4radial thrusts while the other bearing in housing 53 may be of the type disclosed in Figs. 1 and 2. with the parts reversed if the central shaft is rotated, designed to take up radial thrusts only.

'I'he construction of the bearing disclosed in Fig. 3 which is designed to take up both axial and radial thrusts will now be described. Whereas, in y shaft. Fixed bearings I6' are provided in engagement with the spherical journal 60 on the lower side thereof and at the lower ends of diameters D' and D" so as to carry the weight of rotating shaft I5', while at the opposite ends of diameters D' and D" there are provided the 1inings I8' yieldably mounted for radial reciprocating movement in a manner similar to the linings I3 of Fig. 2. 'lhe linings I8' are fixed to cylinders 24' operating within cylindrical bores Il' against the action of springs 25' interposed between the sleeves 24' and nxed heads 22'. Clearances are of the order described in connection with the Figs. 1 and 2 forms.

It will now be seen that the diametrical lines D' and D" may be considered vectors or comvposite forces consisting of a force D which is the tendency of the unbalance of the shaft to let up vibration is overcome by reason of the arrangement of the nxed bearing points l.' and the yielding bearing points Il'. This is of considerable importance in machines such as the grinder shown in Fig. 4, for the reasons hereinbefore stated.

In accordance with the provisions of the patent statutes, we have herein described the principle and operation of our invention, together with the apparatus which we now consider to represent the best embodiment thereof, but we desire to have it understood that the apparatus shown is only illustrative and that the invention can be carried out by other equivalent means. Also, while it is designed to use the various features and elements in the combination and relations described, some of these may be altered and others omitted without interfering with the more general results outlined, and the invention extendsto such use.

Having described our invention, what we claim and desire to secure by Letters Patent is:

1. A high speed bearing for rotors, this bearing comprising a plurality of spaced bearing elements adapted to engage the rotor, means for supportingcertain of the elements xedly, and means for supporting the remainderof the elements yieldably, the yieldable supporting means being inclined in opposite directions at an acute angle with respect to the longitudinal axis of the rotor, whereby these elements yield radially to, and in either direction axially of, the longitudinal axis of the rotor. l

2. A high speed bearing for rotors, this bearing comprising a plurality of pads of relatively short circumferential length, the rotor being supported solely by the pads, a. fixed support for the pads, the pads being completely embedded in the support below the surface of the support except for the bearing surfaces whereby all of the pads are fixed against yielding movement circumferentially of the rotor, certain of the pads being fixed in the support also against radial movement, and means whereby certain other of the pads are yieldably mounted in the support for radial movement.

3. A high speed bearing for rotors, this bearing comprising a plurality of spaced bearing elements adapted to engage the rotor, each of said elements being oi relatively short circumferential length, means for supporting certain of the elements ilxedly, and means for supporting the remainder of the elements yieldably, the yieldable supporting means being inclined in opposite directions at an acute angle with respect to`the longitudinal axis of the rotor, whereby these elements yield radially to, and in'either direction 

